JP6382871B2 - Connecting rod and internal combustion engine - Google Patents

Connecting rod and internal combustion engine Download PDF

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JP6382871B2
JP6382871B2 JP2016039599A JP2016039599A JP6382871B2 JP 6382871 B2 JP6382871 B2 JP 6382871B2 JP 2016039599 A JP2016039599 A JP 2016039599A JP 2016039599 A JP2016039599 A JP 2016039599A JP 6382871 B2 JP6382871 B2 JP 6382871B2
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eccentric
bearing eye
end bearing
small end
connecting rod
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JP2016160940A (en
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ポール ミヒャエル
ポール ミヒャエル
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Dr Ing HCF Porsche AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B31/00—Component parts, details, or accessories not provided for in, or of interest apart from, other groups
    • F01B31/14—Changing of compression ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/045—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable connecting rod length
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/32—Engines characterised by connections between pistons and main shafts and not specific to preceding main groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
    • F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C7/00—Connecting-rods or like links pivoted at both ends; Construction of connecting-rod heads
    • F16C7/06—Adjustable connecting-rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C9/00—Bearings for crankshafts or connecting-rods; Attachment of connecting-rods
    • F16C9/04—Connecting-rod bearings; Attachments thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/042—Guidance of lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0467—Elements of gearings to be lubricated, cooled or heated
    • F16H57/0469—Bearings or seals
    • F16H57/0471—Bearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits
    • F01M2011/027—Arrangements of lubricant conduits for lubricating connecting rod bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/22—Internal combustion engines

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Description

本発明は、内燃機関用の連結ロッドおよび内燃機関に関する。   The present invention relates to a connecting rod for an internal combustion engine and an internal combustion engine.

図１は、（特許文献１）から公知の、圧縮比を調整可能な内燃機関の連結ロッド（コネクティングロッド）を示している。このように、連結ロッド１０は、大端部ベアリングアイ１１および小端部ベアリングアイ１２を有し、大端部ベアリングアイ１１は、連結ロッド１０をクランクシャフト（図１には示していない）に取り付けるために使用され、小端部ベアリングアイ１２は、連結ロッド１０を内燃機関のシリンダピストン（図１には示していない）に取り付けるために使用される。連結ロッド１０は、偏心器（偏心カム、図示せず）、偏心レバー１４、および偏心ロッド１５、１６を有する偏心調整装置１３をあてがわれている。偏心レバー１４は、小端部ベアリングアイ１２の中心１７に対して偏心して配置された、中心１８を有する開孔を有し、偏心レバー１４の開孔は偏心器を収容し、偏心器の開孔は、ピストンピンを収容している。偏心調整装置１３は、連結ロッド有孔長ｌeffを調整するために使用され、連結ロッド長は、大端部ベアリングアイ１１の中心１９から偏心レバー１４の開孔の中心１８までの距離を意味すると解釈すべきである。偏心本体１４を回転させるために、ひいては、連結ロッド有効長ｌeffを変えるために、偏心ロッド１５、１６を移動させることができる。各偏心ロッド１５、１６は、案内されて油圧チャンバ２２、２３内を移動できるピストン２０、２１をあてがわれている。偏心ロッド１５、１６にあてがわれたピストン２０、２１に作用する油圧は、油圧チャンバ２２、２３内に広がり、偏心ロッド１５、１６は、油圧チャンバ内の油量に応じて、移動できたり、または移動できなかったりする。 FIG. 1 shows a connecting rod (connecting rod) of an internal combustion engine which is known from (Patent Document 1) and whose compression ratio can be adjusted. Thus, the connecting rod 10 has the large end bearing eye 11 and the small end bearing eye 12, and the large end bearing eye 11 attaches the connecting rod 10 to the crankshaft (not shown in FIG. 1). A small end bearing eye 12 is used to attach the connecting rod 10 to the cylinder piston (not shown in FIG. 1) of the internal combustion engine. The connecting rod 10 is provided with an eccentric adjusting device 13 having an eccentric (an eccentric cam, not shown), an eccentric lever 14 and eccentric rods 15 and 16. The eccentric lever 14 has an aperture having a center 18 arranged eccentrically with respect to the center 17 of the small end bearing eye 12, the aperture of the eccentric lever 14 accommodating the eccentric and opening the eccentric. The hole accommodates the piston pin. The eccentricity adjusting device 13 is used to adjust the connecting rod perforated length l eff , which means the distance from the center 19 of the large end bearing eye 11 to the center 18 of the opening of the eccentric lever 14. That should be interpreted. In order to rotate the eccentric body 14, the eccentric rods 15, 16 can thus be moved in order to change the connecting rod effective length leff . Each eccentric rod 15, 16 is assigned a piston 20, 21 that is guided and can move within the hydraulic chambers 22, 23. The hydraulic pressure acting on the pistons 20 and 21 applied to the eccentric rods 15 and 16 spreads in the hydraulic chambers 22 and 23, and the eccentric rods 15 and 16 can move according to the amount of oil in the hydraulic chambers. Or you cannot move.

偏心調整装置１３の調整は、内燃機関の動作サイクル時に、偏心調整装置１３に作用する内燃機関の慣性力および負荷力の働きによって開始される。動作サイクル時に、偏心調整装置１３に作用する力の作用方向は連続的に変わる。調整動作は、油圧油から作用を受けて、偏心ロッド１５、１６に作用するピストン２０、２１によって補助され、ピストン２０、２１は、偏心調整装置１３に作用する力の、力の作用方向が変わることに起因する偏心調整装置１３の戻りを妨げる。ピストン２０、２１と相互作用する偏心ロッド１５、１６は、両側で偏心本体１４に取り付けられている。ピストン２０、２１が中で案内される油圧チャンバ２２、２３には、大端部ベアリングアイ１１から油圧管２４、２５を介して油圧油を供給することができる。逆止弁２６、２７は、油圧油が油圧チャンバ２２、２３から油圧管２４、２５に逆流するのを防止する。切換弁２９は、連結ロッド１０の穴２８に収容されており、切換弁２９の切換位置により、油圧チャンバ２２、２３のどちらに油圧油を充填し、油圧チャンバ２２、２３のどちらを空にするかが決まり、偏心調整装置１３の調整方向または回転方向はそれによって決まる。この場合に、油圧チャンバ２２、２３は、それぞれ流体管３０、３１を介して、切換弁２９を収容した穴２８と通じている。切換弁２９の駆動手段３２、ばね装置３３、および制御ピストン３４が、図１に概略的に示されており、切換弁２９のこれらの構成要素の動作は、（特許文献１）からすでに公知である。   The adjustment of the eccentricity adjusting device 13 is started by the action of the inertial force and load force of the internal combustion engine acting on the eccentricity adjusting device 13 during the operation cycle of the internal combustion engine. During the operation cycle, the direction of the force acting on the eccentricity adjusting device 13 changes continuously. The adjusting operation is assisted by the pistons 20 and 21 acting on the eccentric rods 15 and 16 under the action of the hydraulic oil, and the pistons 20 and 21 change the force acting direction of the force acting on the eccentricity adjusting device 13. This prevents the eccentric adjustment device 13 from returning. The eccentric rods 15 and 16 that interact with the pistons 20 and 21 are attached to the eccentric body 14 on both sides. Hydraulic oil can be supplied from the large end bearing eye 11 through the hydraulic pipes 24 and 25 to the hydraulic chambers 22 and 23 in which the pistons 20 and 21 are guided. The check valves 26 and 27 prevent the hydraulic oil from flowing back from the hydraulic chambers 22 and 23 to the hydraulic pipes 24 and 25. The switching valve 29 is accommodated in the hole 28 of the connecting rod 10. Depending on the switching position of the switching valve 29, either of the hydraulic chambers 22, 23 is filled with hydraulic oil, and which of the hydraulic chambers 22, 23 is emptied. The direction of adjustment or the direction of rotation of the eccentricity adjusting device 13 is determined thereby. In this case, the hydraulic chambers 22 and 23 communicate with the hole 28 that accommodates the switching valve 29 via the fluid pipes 30 and 31, respectively. The drive means 32 of the switching valve 29, the spring device 33 and the control piston 34 are shown schematically in FIG. 1, and the operation of these components of the switching valve 29 is already known from US Pat. is there.

上記のように、油圧チャンバ２２、２３内で案内されるピストン２０、２１に作用する油圧油は、大端部ベアリングアイ１１から油圧管２４、２５を介して、油圧チャンバ２２、２３に供給され、連結ロッド１０は、連結ロッドベアリングシェル３５が、クランクシャフト（図１には示していない）、すなわち、クランクシャフトのクランクシャフトベアリングジャーナルと大端部ベアリングアイとの間に配置されるように、大端部ベアリングアイ１１を用いてクランクシャフトと係合する。   As described above, the hydraulic oil acting on the pistons 20 and 21 guided in the hydraulic chambers 22 and 23 is supplied from the large end bearing eye 11 to the hydraulic chambers 22 and 23 via the hydraulic pipes 24 and 25. The connecting rod 10 is such that the connecting rod bearing shell 35 is disposed between the crankshaft (not shown in FIG. 1), ie, the crankshaft bearing journal of the crankshaft and the large end bearing eye. A large end bearing eye 11 is used to engage the crankshaft.

独国特許出願公開第１０ ２０１０ ０１６ ０３７Ａ１号明細書German Patent Application Publication No. 10 2010 016 037A1

本発明の目的は、新規の内燃機関および新規の連結ロッドを提供することである。   An object of the present invention is to provide a novel internal combustion engine and a novel connecting rod.

この目的は、請求項１に記載の連結ロッドによって達成される。本発明によれば、小端部ベアリングアイと偏心器（偏心カム）との間に潤滑油膜を形成することを可能にする潤滑油穴が、小端部ベアリングアイに形成され、小端部ベアリングアイは、偏心器を収容するように機能する、小端部ベアリングアイの開孔に対する潤滑油穴が、前記ベアリングアイに形成された領域において、前記ベアリングアイの他の領域の壁厚よりも厚い壁厚を有する。   This object is achieved by a connecting rod according to claim 1. According to the present invention, a lubricating oil hole that enables a lubricating oil film to be formed between the small end bearing eye and the eccentric (eccentric cam) is formed in the small end bearing eye. The eye functions to accommodate the eccentric, and the lubricating oil hole for the small-end bearing eye opening is thicker than the wall thickness of the other area of the bearing eye in the area where the bearing eye is formed. Has a wall thickness.

本発明は、小端部ベアリングアイと、小端部ベアリングアイの開孔に収容された偏心器との間の接触領域の有益な潤滑を可能にする。潤滑油穴によってもたらされる小端部ベアリングアイの脆弱化を補償するために、前記ベアリングアイは、偏心器を収容するように機能する開孔に対する潤滑油穴が、前記ベアリングアイに形成された領域において、隣接する、または近接する領域の半径方向の壁厚よりも厚い半径方向の壁厚を有する。潤滑油穴が、小端部ベアリングアイに形成された領域以外の小端部ベアリングアイの領域の半径方向の壁厚を薄くすることにより、一方で、連結ロッドの重量を削減し、他方で、小端部ベアリングアイと偏心調整装置の偏心ロッドとの間に十分なすき間をもたらすことが可能である。   The present invention allows beneficial lubrication of the contact area between the small end bearing eye and the eccentric located in the aperture of the small end bearing eye. In order to compensate for the weakening of the small end bearing eye caused by the lubricating oil hole, the bearing eye is a region where a lubricating oil hole is formed in the bearing eye for an opening that serves to accommodate an eccentric. At a radial wall thickness greater than the radial wall thickness of adjacent or adjacent regions. Lubricating oil holes reduce the weight of the connecting rod on the one hand, by reducing the radial wall thickness in the region of the small end bearing eye other than the region formed in the small end bearing eye, It is possible to provide a sufficient clearance between the small end bearing eye and the eccentric rod of the eccentricity adjusting device.

発展形態によれば、小端部ベアリングアイは、偏心調整装置の伸長した偏心ロッドと正反対に位置する、または伸長した偏心ロッドに対向する領域において、潤滑油穴が、小端部ベアリングアイに形成された領域の半径方向の壁厚よりも薄い半径方向の壁厚を有する。これは、遠心ロッドと小端部ベアリングアイとの間にすき間をもたらし、重量を削減するのに寄与する。   According to a development, the small-end bearing eye is formed in the small-end bearing eye in a region that is located diametrically opposite or opposite to the extended eccentric rod of the eccentric adjustment device. Having a radial wall thickness that is less than the radial wall thickness of the formed region. This provides a gap between the centrifugal rod and the small end bearing eye, which contributes to weight reduction.

発展形態によれば、小端部ベアリングアイの半径方向に延び、小端部ベアリングアイの周方向に離間した少なくとも２つの潤滑油穴が、小端部ベアリングアイに形成され、小端部ベアリングアイは、潤滑油穴が、前記ベアリングアイに形成された領域において、これらの領域間で、小端部ベアリングアイの周方向に配置された領域の壁厚よりも厚い壁厚を有する。これは、特に、連結ロッドの重量の削減に寄与する。   According to a development, at least two lubricating oil holes extending in the radial direction of the small end bearing eye and spaced apart in the circumferential direction of the small end bearing eye are formed in the small end bearing eye, In the regions where the lubricating oil holes are formed in the bearing eye, the wall thickness between these regions is greater than the wall thickness of the region disposed in the circumferential direction of the small end bearing eye. This particularly contributes to a reduction in the weight of the connecting rod.

有益な発展形態によれば、小端部ベアリングアイにおける、壁厚が異なる領域間の移行部は、連続的に、したがって、不連続点のない態様で形成される。それにより、小端部ベアリングアイの壁厚の変化による応力のさらなる増大なしに、小端部ベアリングアイの材料に対する負荷を均一にすることが可能である。   According to a beneficial development, the transition between regions of different wall thickness in the small end bearing eye is formed continuously and thus in a manner free of discontinuities. Thereby, it is possible to make the load on the material of the small end bearing eye uniform without any further increase in stress due to changes in the wall thickness of the small end bearing eye.

内燃機関は請求項５で規定される。   An internal combustion engine is defined in claim 5.

本発明の好ましい発展形態が、従属請求項および以下の説明から明らかになるであろう。本発明の例示的な実施形態が、その実施形態に制限されることなく、図面を用いてさらに詳細に説明される。   Preferred developments of the invention will become apparent from the dependent claims and the following description. Exemplary embodiments of the present invention are described in more detail with reference to the drawings without being limited to the embodiments.

圧縮比を調整可能な、先行技術から公知の内燃機関の連結ロッドを示している。1 shows a connecting rod of an internal combustion engine known from the prior art with an adjustable compression ratio. 連結ロッドの細部を示している。The details of the connecting rod are shown. 本発明による連結ロッドの細部を示している。2 shows details of a connecting rod according to the invention.

圧縮比が調整可能な内燃機関は、少なくとも１つのシリンダ、好ましくは複数のシリンダを有する。各シリンダは、連結ロッド１０によって内燃機関のクランクシャフトに連結されるピストンを有する。各連結ロッド１０は、一端に小端部ベアリングアイ１２、および反対側の端部に大端部ベアリングアイ１１を有する。それぞれの連結ロッド１０は、連結ロッドベアリングシェルが、クランクシャフトベアリングジャーナルと大端部ベアリングアイとの間に配置されるように、大端部ベアリングアイ１１を用いて、クランクシャフトベアリングジャーナルと係合し、潤滑油膜は、連結ロッドベアリングシェルとクランクシャフトベアリングジャーナルとの間に形成することができる。   An internal combustion engine with adjustable compression ratio has at least one cylinder, preferably a plurality of cylinders. Each cylinder has a piston connected to the crankshaft of the internal combustion engine by a connecting rod 10. Each connecting rod 10 has a small end bearing eye 12 at one end and a large end bearing eye 11 at the opposite end. Each connecting rod 10 is engaged with a crankshaft bearing journal using a large end bearing eye 11 such that a connecting rod bearing shell is disposed between the crankshaft bearing journal and the large end bearing eye. The lubricating oil film can be formed between the connecting rod bearing shell and the crankshaft bearing journal.

圧縮比が調整可能な内燃機関は、それぞれの連結ロッド１０の連結ロッド有効長を調整するために、各連結ロッド１０の領域に偏心調整装置１３を有する。   The internal combustion engine capable of adjusting the compression ratio has an eccentricity adjusting device 13 in the region of each connecting rod 10 in order to adjust the connecting rod effective length of each connecting rod 10.

偏心調整装置１３は、偏心器、偏心レバー１４、および偏心ロッド１５、１６を有し、偏心ロッド１５、１６は、圧縮比を調整するために、偏心ロッドと相互作用する油圧チャンバ内に広がる油圧に従って移動することができる。偏心ロッド１５、１６と相互作用する油圧チャンバには、それぞれの連結ロッドの大端部ベアリングアイ１１から油圧油を供給することができる。偏心調整装置の調整は、内燃機関の慣性力および負荷力の働きによって開始される。   The eccentricity adjusting device 13 has an eccentric, an eccentric lever 14, and eccentric rods 15, 16, which are spread in a hydraulic chamber that interacts with the eccentric rod to adjust the compression ratio. Can move according to. Hydraulic oil can be supplied to the hydraulic chambers that interact with the eccentric rods 15, 16 from the large end bearing eye 11 of the respective connecting rods. Adjustment of the eccentricity adjusting device is started by the action of the inertial force and load force of the internal combustion engine.

偏心レバー１４および小端部ベアリングアイ１２はそれぞれ、偏心器３６を収容する開孔または穴を有し、偏心器３６としては、ピストンピン３７を収容するように機能する開孔または穴を有する。   Each of the eccentric lever 14 and the small end bearing eye 12 has an opening or hole for receiving the eccentric 36, and the eccentric 36 has an opening or hole that functions to receive the piston pin 37.

少なくとも小端部ベアリングアイ１２と偏心器３６との間で潤滑油膜が形成されるのを可能にする潤滑油穴３８、３９と、好ましくは、偏心器３６とピストンピン３７との間で同様に潤滑油膜が形成されるのを可能にする潤滑油穴４０、４１とが、小端部ベアリングアイ１２、および、好ましくは、さらに偏心器３６に形成される。偏心調整装置１３の終端位置において、および偏心調整装置１３の調整時に、潤滑油穴３８、３９、４０、４１は、小端部ベアリングアイ１２と偏心器３６との間、および、好ましくは偏心器３６とピストンピン３７との間の接触点の良好な潤滑を可能にする。   Lubricant holes 38, 39 that allow a lubricant film to be formed at least between the small end bearing eye 12 and the eccentric 36, and preferably between the eccentric 36 and the piston pin 37 as well. Lubricating oil holes 40, 41 that allow a lubricating oil film to be formed are formed in the small end bearing eye 12, and preferably further in the eccentric 36. At the end position of the eccentricity adjusting device 13 and when adjusting the eccentricity adjusting device 13, the lubricating oil holes 38, 39, 40, 41 are between the small end bearing eye 12 and the eccentric 36, and preferably the eccentric. Allows good lubrication of the contact point between 36 and the piston pin 37.

図２および図３によれば、２つの潤滑油穴３８、３９は、小端部ベアリングアイ１２に形成され、２つの潤滑油穴４０、４１は、偏心器３６に形成されている。   2 and 3, the two lubricating oil holes 38, 39 are formed in the small end bearing eye 12, and the two lubricating oil holes 40, 41 are formed in the eccentric 36.

潤滑油穴３８、３９、４０、４１は、偏心器３６または偏心調整装置１３の第１の終端位置において、偏心器３６の第１の潤滑油穴４０が、小端部ベアリングアイ１２の第１の潤滑油穴３８と一列に整列するように、小端部ベアリングアイ１２および偏心器３６に形成され、その結果として、第１の終端位置（図２を参照のこと）にある前記穴によって、偏心器３６とピストンピン３７との間に潤滑油膜を形成することができる。潤滑油穴３８、３９、４０、４１は、さらに、偏心器３６または偏心調整装置１３の第２の終端位置において、偏心器３６の第２の潤滑油穴４１が、小端部ベアリングアイ１２の第２の潤滑油穴３９と一列に整列するように、小端部ベアリングアイ１２および偏心器３６に形成され、潤滑油膜が、第２の終端位置にある前記穴によって、偏心器３６とピストンピン３７との間に形成されるのを可能にする。偏心器３６または偏心調整装置１３の第１の終端位置では、偏心器３６の第２の潤滑油穴４１は、小端部ベアリングアイ１２の第２の潤滑油穴３９と一列に整列せず、したがって、この場合に、潤滑油膜は、第１の終端位置にある小端部ベアリングアイ１２の第２の潤滑油穴３９によって、小端部ベアリングアイ１２と偏心器３６との間に形成することができる。偏心器３６または偏心調整装置１３の第２の終端位置では、偏心器３６の第１の潤滑油穴４０は、小端部ベアリングアイ１２の第１の潤滑油穴３８と一列に整列せず、したがって、この場合に、潤滑油膜は、第２の終端位置にある小端部ベアリングアイ１２の第１の潤滑油穴３８によって、小端部ベアリングアイ１２と偏心器３６との間に形成することができる。偏心調整装置１３の終端位置において、および偏心調整装置１３の調整時に、潤滑油穴３８、３９、４０、４１は、小端部ベアリングアイ１２と偏心器３６との間、および偏心器３６とピストンピン３７との間の接触点の特に有益な潤滑を可能にする。   The lubricating oil holes 38, 39, 40, 41 are arranged at the first end position of the eccentric 36 or the eccentric adjusting device 13, and the first lubricating oil hole 40 of the eccentric 36 is connected to the first end of the small end bearing eye 12. Are formed in the small end bearing eye 12 and the eccentric 36 so as to be aligned with the lubricating oil holes 38 of the first end position (see FIG. 2). A lubricating oil film can be formed between the eccentric 36 and the piston pin 37. The lubricating oil holes 38, 39, 40, 41 are further provided at the second terminal position of the eccentric 36 or the eccentricity adjusting device 13 so that the second lubricating oil hole 41 of the eccentric 36 is connected to the small end bearing eye 12. A small end bearing eye 12 and an eccentric 36 are formed on the small end bearing eye 12 and the eccentric 36 so as to align with the second lubricating oil hole 39, and the lubricant film is formed by the hole at the second terminal position by the eccentric 36 and the piston pin. 37 can be formed between. In the first terminal position of the eccentric 36 or the eccentric adjustment device 13, the second lubricating oil hole 41 of the eccentric 36 is not aligned with the second lubricating oil hole 39 of the small end bearing eye 12, Therefore, in this case, the lubricating oil film is formed between the small end bearing eye 12 and the eccentric 36 by the second lubricating oil hole 39 of the small end bearing eye 12 at the first terminal position. Can do. In the second terminal position of the eccentric 36 or the eccentric adjusting device 13, the first lubricating oil hole 40 of the eccentric 36 is not aligned with the first lubricating oil hole 38 of the small end bearing eye 12, Therefore, in this case, the lubricating oil film is formed between the small end bearing eye 12 and the eccentric 36 by the first lubricating oil hole 38 of the small end bearing eye 12 at the second terminal position. Can do. At the end position of the eccentricity adjusting device 13 and when adjusting the eccentricity adjusting device 13, the lubricating oil holes 38, 39, 40, 41 are located between the small end bearing eye 12 and the eccentric 36 and between the eccentric 36 and the piston. A particularly beneficial lubrication of the contact point between the pins 37 is possible.

小端部ベアリングアイ１２の潤滑油穴３８、３９と、好ましくは偏心器３６に存在する潤滑油穴４０、４１とは、それぞれ、偏心器３６の半径方向および小端部ベアリングアイ１２の半径方向に延びている。偏心器３６の第１の潤滑油穴４０および小端部ベアリングアイ１２の第１の潤滑油穴３８は、同じ直径を有するのが好ましい。偏心器３６の第２の潤滑油穴４１および小端部ベアリングアイ１２の第２の潤滑油穴３９は、同様に、同じ直径を有するのが好ましい。   Lubricating oil holes 38, 39 of the small end bearing eye 12 and preferably lubricating oil holes 40, 41 present in the eccentric 36 are respectively in the radial direction of the eccentric 36 and in the radial direction of the small end bearing eye 12. It extends to. The first lubricating oil hole 40 of the eccentric 36 and the first lubricating oil hole 38 of the small end bearing eye 12 preferably have the same diameter. Similarly, the second lubricating oil hole 41 of the eccentric 36 and the second lubricating oil hole 39 of the small end bearing eye 12 preferably have the same diameter.

すでに説明したように、小端部ベアリングアイ１２と偏心器３６との間に潤滑油膜を形成することを可能にする潤滑油穴３８、３９は、小端部ベアリングアイ１２に形成されている。   As described above, the lubricating oil holes 38 and 39 that allow a lubricating oil film to be formed between the small end bearing eye 12 and the eccentric 36 are formed in the small end bearing eye 12.

本発明によれば、図３から分かるように、小端部ベアリングアイ１２は、偏心器３６を収容するように機能する、小端部ベアリングアイ１２の開孔または穴に対する潤滑油穴３８、３９が、前記ベアリングアイ１２に形成された領域において、その領域に隣接する、または近接する領域の半径方向の壁厚よりも厚い半径方向の壁厚を有するとさらに想定されている。   In accordance with the present invention, as can be seen from FIG. 3, the small end bearing eye 12 serves to accommodate the eccentric 36, and the lubricating oil holes 38, 39 to the openings or holes in the small end bearing eye 12. However, it is further assumed that the region formed in the bearing eye 12 has a radial wall thickness that is greater than the radial wall thickness of the region adjacent or adjacent to that region.

半径Ｒ１によって、図２は、偏心器３６を収容した、小端部ベアリングアイ１２の穴または開孔の半径を示し、半径Ｒ２によって、図２は、小端部ベアリングアイ１２の半径を示しており、図２では、半径Ｒ１、Ｒ２間の差、したがって、半径方向に見た小端部ベアリングアイ１２の壁厚は、小端部ベアリングアイ１２の外周にわたって、ほとんど完全に同じであり、連結ロッド１０の連結ロッド本体への移行領域のみ変わっている。   By radius R 1, FIG. 2 shows the radius of the hole or aperture of the small end bearing eye 12 containing the eccentric 36, and by radius R 2, FIG. 2 shows the radius of the small end bearing eye 12. In FIG. 2, the difference between the radii R1, R2 and thus the wall thickness of the small end bearing eye 12 seen in the radial direction is almost completely the same over the outer circumference of the small end bearing eye 12, Only the transition region of the rod 10 to the connecting rod body is changed.

本発明によれば、図３から分かるように、小端部ベアリングアイ１２は、図２とは異なる輪郭を有し、したがって、潤滑油穴３８、３９が、前記ベアリングアイに形成された領域の小端部ベアリングアイ１２の半径方向の壁厚は、その領域に隣接する、または近接する領域の半径方向の壁厚よりも厚い。   According to the present invention, as can be seen from FIG. 3, the small end bearing eye 12 has a different profile than that of FIG. 2, so that the lubricating oil holes 38, 39 are in the region formed in the bearing eye. The radial wall thickness of the small end bearing eye 12 is greater than the radial wall thickness of the region adjacent to or adjacent to that region.

それと共に、図３は、２つの潤滑油穴３８、３９が小端部ベアリングアイ１２に形成され、前記穴はそれぞれ、小端部ベアリングアイ１２の半径方向に延び、小端部ベアリングアイ１２の周方向に離間することを示している。小端部ベアリングアイ１２のうちの潤滑油穴３８、３９が前記ベアリングアイに形成された領域では、小端部ベアリングアイ１２は、小端部ベアリングアイ１２の周方向に見て、これらの領域間に配置された領域４３の半径方向の壁厚よりも厚い半径方向の壁厚を有する。したがって、図３から分かるように、ベアリングアイの外形は、周方向に見て、潤滑油穴３８、３９間に配置された小端部ベアリングアイ１２の領域４３で、半径Ｒ２に対して半径方向内側に後退することができる。   3 shows that two lubricating oil holes 38, 39 are formed in the small end bearing eye 12, each extending in the radial direction of the small end bearing eye 12, and It shows that they are separated in the circumferential direction. In the region where the lubricating oil holes 38 and 39 of the small end bearing eye 12 are formed in the bearing eye, the small end bearing eye 12 is viewed in the circumferential direction of the small end bearing eye 12. It has a radial wall thickness that is greater than the radial wall thickness of the region 43 disposed therebetween. Therefore, as can be seen from FIG. 3, the outer shape of the bearing eye is the radial direction with respect to the radius R2 in the region 43 of the small end bearing eye 12 disposed between the lubricating oil holes 38, 39 when viewed in the circumferential direction. Can be retracted inward.

図３では、小端部ベアリングアイ１２は、それぞれの偏心ロッド１５、１６が伸長した状態で、それぞれの偏心ロッド１５、１６の正反対に位置する、またはそれらの偏心ロッド１５、１６に対向する領域４４、４５において、潤滑油穴３８、３９が、小端部ベアリングアイ１２に形成された領域の半径方向の壁厚よりも薄い半径方向の壁厚を有するとさらに想定されている。これらの領域４４、４５では、小端部ベアリングアイ１２の外形は、半径Ｒ２に対して半径方向内側に後退している。   In FIG. 3, the small-end bearing eye 12 is a region where the eccentric rods 15, 16 are extended and located opposite to or opposite to the eccentric rods 15, 16. 44 and 45, it is further assumed that the lubricating oil holes 38 and 39 have a radial wall thickness that is less than the radial wall thickness of the region formed in the small end bearing eye 12. In these regions 44 and 45, the outer shape of the small end bearing eye 12 recedes inward in the radial direction with respect to the radius R2.

領域４４、４５の小端部ベアリングアイ１２の壁厚をより薄くすることは、特に、偏心ロッド１５、１６に十分なすき間をもたらし、さらに、重量を削減するのに寄与する。領域４３の小端部ベアリングアイ１２の壁厚をより薄くすることは、重量を削減するのに寄与する。   Reducing the wall thickness of the small end bearing eye 12 in the regions 44, 45 provides, in particular, sufficient clearance for the eccentric rods 15, 16, and further contributes to weight reduction. Reducing the wall thickness of the small end bearing eye 12 in the region 43 contributes to weight reduction.

本発明によれば、小端部ベアリングアイ１２の壁厚は、負荷に対して最適化した態様で適宜具現化され、小端部ベアリングアイ１２の厚い方の半径方向の壁厚は、潤滑油穴３８、３９の領域に隣接する領域よりも潤滑油穴３８、３９の領域に付与される。それにより、潤滑油穴３８、３９の領域において、小端部ベアリングアイ１２および連結ロッド１０の十分な強度または安定性が保証され、さらに、連結ロッド１０に対して低重量が保証され、他方で、小端部ベアリングアイ１２に対する十分なすき間が偏心ロッド１５、１６にもたらされる。   According to the present invention, the wall thickness of the small end bearing eye 12 is appropriately embodied in a manner optimized for the load, and the thicker radial wall thickness of the small end bearing eye 12 is the lubricating oil. It is applied to the region of the lubricating oil holes 38 and 39 rather than the region adjacent to the region of the holes 38 and 39. Thereby, sufficient strength or stability of the small end bearing eye 12 and the connecting rod 10 is ensured in the region of the lubricating oil holes 38, 39, and furthermore, a low weight is guaranteed for the connecting rod 10, while Sufficient clearance for the small end bearing eye 12 is provided in the eccentric rods 15,16.

小端部ベアリングアイ１２における、半径方向の壁厚が異なる領域間の移行部は、連続的に、したがって、不連続点のない態様で形成されるのが好ましい。結果的に、小端部ベアリングアイ１２における、半径方向の壁厚が異なる領域間の不連続な移行が回避される。それにより、壁厚の変化による応力のさらなる増大なしに、小端部ベアリングアイ１２の材料に対する負荷を均一にすることができる。   The transition between regions of different radial wall thicknesses in the small end bearing eye 12 is preferably formed continuously and thus in a manner free of discontinuities. As a result, discontinuous transitions between regions of different radial wall thickness in the small end bearing eye 12 are avoided. Thereby, the load on the material of the small end bearing eye 12 can be made uniform without further increase in stress due to the change in wall thickness.

１０ 連結ロッド
１１ 大端部ベアリングアイ
１２ 小端部ベアリングアイ
１３ 偏心調整装置
１４ 偏心レバー
１５ 偏心ロッド
１６ 偏心ロッド
２２ 油圧チャンバ
２３ 油圧チャンバ
３６ 偏心器
３７ ピストンピン
３８ 潤滑油穴
３９ 潤滑油穴
４３ 領域
４４ 領域
４５ 領域 DESCRIPTION OF SYMBOLS 10 Connecting rod 11 Large end bearing eye 12 Small end bearing eye 13 Eccentricity adjusting device 14 Eccentric lever 15 Eccentric rod 16 Eccentric rod 22 Hydraulic chamber 23 Hydraulic chamber 36 Eccentricator 37 Piston pin 38 Lubricating oil hole 39 Lubricating oil hole 43 Area 44 areas 45 areas

Claims (4)

クランクシャフトに取り付けるための大端部ベアリングアイ（１１）と、シリンダのピストンに取り付けるための小端部ベアリングアイ（１２）と、連結ロッド有効長を調整するための偏心調整装置（１３）とを有する連結ロッド（１０）であって、
前記偏心調整装置（１３）は、前記偏心調整装置（１３）の偏心レバー（１４）と係合する偏心ロッド（１５、１６）を有し、前記偏心調整装置（１３）は、前記偏心レバー（１４）および前記小端部ベアリングアイ（１２）の開孔内で案内され、ピストンピン（３７）を収容するための開孔を有する偏心器（３６）を有する、連結ロッド（１０）において、
少なくとも２つの位置にて、前記小端部ベアリングアイ（１２）と前記偏心器（３６）との間に潤滑油膜を形成することを可能にする複数の潤滑油穴（３８、３９）が、前記小端部ベアリングアイ（１２）に形成されることと、前記小端部ベアリングアイ（１２）は、前記偏心器（３６）を収容するように機能することと、前記小端部ベアリングアイ（１２）の前記開孔に対する前記潤滑油穴（３８、３９）が、前記ベアリングアイに形成される領域において、前記ベアリングアイの隣接する領域の半径方向の壁厚よりも厚い半径方向の壁厚を有しており、
前記小端部ベアリングアイ（１２）における、壁厚が異なる領域間の移行部は前記潤滑油穴（３８、３９）に向って、前記壁厚が連続的に且つ単調増加していることとを特徴とする連結ロッド（１０）。 A large end bearing eye (11) for attaching to the crankshaft, a small end bearing eye (12) for attaching to the piston of the cylinder, and an eccentricity adjusting device (13) for adjusting the effective length of the connecting rod. A connecting rod (10) comprising:
The eccentric adjustment device (13) has an eccentric rod (15, 16) that engages with an eccentric lever (14) of the eccentric adjustment device (13), and the eccentric adjustment device (13) 14) and a connecting rod (10) having an eccentric (36) guided in an aperture in said small end bearing eye (12) and having an aperture for receiving a piston pin (37),
A plurality of lubricating oil holes (38, 39) that enable a lubricating oil film to form between the small end bearing eye (12) and the eccentric (36) in at least two positions, Formed in the small end bearing eye (12), the small end bearing eye (12) functions to receive the eccentric (36), and the small end bearing eye (12). ) is the lubricating oil hole for the opening of the (38, 39), in the region formed in the bearing eye, it has a thick radial wall thickness than the radial wall thickness of the adjacent region of the bearing eye And
In the small-end bearing eye (12), the transition between the regions having different wall thicknesses is continuously and monotonically increasing toward the lubricating oil holes (38, 39). Feature connecting rod (10). 前記小端部ベアリングアイ（１２）の半径方向に延び、前記小端部ベアリングアイ（１２）の周方向に離間した少なくとも２つの潤滑油穴（３８、３９）が、前記小端部ベアリングアイ（１２）に形成され、前記小端部ベアリングアイ（１２）は、前記潤滑油穴（３８、３９）が前記ベアリングアイに形成される領域において、前記小端部ベアリングアイ（１２）の周方向に見て、前記領域間に配置された領域（４３）の半径方向の壁厚よりも厚い半径方向の壁厚を有することを特徴とする、請求項１に記載の連結ロッド。   At least two lubricating oil holes (38, 39) extending in the radial direction of the small end bearing eye (12) and spaced apart in the circumferential direction of the small end bearing eye (12) are provided in the small end bearing eye ( 12), and the small end bearing eye (12) is formed in the circumferential direction of the small end bearing eye (12) in the region where the lubricating oil holes (38, 39) are formed in the bearing eye. The connecting rod according to claim 1, characterized in that it has a radial wall thickness that is greater than the radial wall thickness of the regions (43) arranged between the regions. 前記小端部ベアリングアイ（１２）は、前記偏心調整装置（１３）の伸長した前記偏心ロッド（１５、１６）と正反対に位置する、または伸長した前記偏心ロッド（１５、１６）に対向する領域において、前記潤滑油穴（３８、３９）が、前記小端部ベアリングアイ（１２）に形成された領域の半径方向の壁厚よりも薄い半径方向の壁厚を有することを特徴とする、請求項１または２に記載の連結ロッド。   The small end bearing eye (12) is located in a region opposite to the extended eccentric rod (15, 16) of the eccentric adjustment device (13) or opposed to the extended eccentric rod (15, 16). Wherein the lubricating oil holes (38, 39) have a radial wall thickness that is less than a radial wall thickness of a region formed in the small end bearing eye (12). Item 3. The connecting rod according to Item 1 or 2. 圧縮比が調整可能な内燃機関であって、少なくとも１つのシリンダと、少なくとも１つの連結ロッド（１０）が係合したクランクシャフトとを有し、前記または各連結ロッド（１０）は、前記連結ロッド（１０）を前記クランクシャフトに取り付けるための大端部ベアリング穴（１１）と、前記連結ロッド（１０）をシリンダのピストンに取り付けるための小端部ベアリング穴（１２）と、連結ロッド有効長を調整するための偏心調整装置（１３）とを有し、前記偏心調整装置（１３）は、偏心レバー（１４）と相互作用する偏心器（３６）と、偏心ロッド（１５、１６）とを有し、前記偏心ロッド（１５、１６）は、前記偏心レバー（１４）と係合し、かつ前記偏心ロッド（１５、１６）と相互作用する油圧チャンバ（２２、２３）内に広がる油圧から作用を受ける、内燃機関において、前記または各連結ロッド（１０）は、請求項１〜３のいずれか１項に記載の通りに設計されることを特徴とする内燃機関。 An internal combustion engine with adjustable compression ratio, comprising at least one cylinder and a crankshaft engaged with at least one connecting rod (10), wherein each or each connecting rod (10) is said connecting rod A large end bearing hole (11) for attaching (10) to the crankshaft, a small end bearing hole (12) for attaching the connecting rod (10) to the piston of the cylinder, and a connecting rod effective length. An eccentric adjusting device (13) for adjusting, the eccentric adjusting device (13) having an eccentric device (36) interacting with the eccentric lever (14) and an eccentric rod (15, 16). The eccentric rods (15, 16) are widened in the hydraulic chambers (22, 23) that engage with the eccentric lever (14) and interact with the eccentric rods (15, 16). That hydraulic acted upon from the internal combustion engine, wherein the or each connecting rod (10) is an internal combustion engine, characterized in that it is designed as described in claim 1.
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